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JP2007533904A - Cooling passage cover for internal combustion engine pistons - Google Patents

Cooling passage cover for internal combustion engine pistons Download PDF

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Publication number
JP2007533904A
JP2007533904A JP2007508723A JP2007508723A JP2007533904A JP 2007533904 A JP2007533904 A JP 2007533904A JP 2007508723 A JP2007508723 A JP 2007508723A JP 2007508723 A JP2007508723 A JP 2007508723A JP 2007533904 A JP2007533904 A JP 2007533904A
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piston
cooling passage
spring
spring metal
thin plate
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JP4598059B2 (en
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シャープ ライナー
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Mahle GmbH
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Mahle GmbH
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F3/00—Pistons 
    • F02F3/16—Pistons  having cooling means
    • F02F3/20—Pistons  having cooling means the means being a fluid flowing through or along piston
    • F02F3/22—Pistons  having cooling means the means being a fluid flowing through or along piston the fluid being liquid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F3/00—Pistons 
    • F02F3/16—Pistons  having cooling means

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)

Abstract

本発明は、ばね金属薄板（１）の形をした内燃機関のピストン（８）のための冷却通路カバーであって、該ばね金属薄板が、摩耗を回避するために支持部の領域において次のように、すなわち、ばね金属薄板（１）の半径方向外側の端面と階段状の凹設部（１９）の半径方向外側の画成部との間に環状の間隙（１２）が生ぜしめられるように、寸法設定されている。  The invention relates to a cooling passage cover for a piston (8) of an internal combustion engine in the form of a spring metal sheet (1), the spring sheet metal in the region of the support in order to avoid wear: That is, an annular gap (12) is formed between the radially outer end face of the spring metal thin plate (1) and the radially outer defined portion of the stepped recess (19). Are dimensioned.

Description

本発明は、請求項１の上位概念部に記載された形式の内燃機関のピストン用の冷却通路カバーに関する。   The present invention relates to a cooling passage cover for a piston of an internal combustion engine of the type described in the superordinate conceptual part of claim 1.

ドイツ連邦共和国特許第４２０８０３７号明細書に基づいて、内燃機関用のピストンのピストンヘッドの領域に、半径方向外側に位置していてピストンスカートに向かって開放する冷却通路を設けることが公知である。冷却通路に導入される冷却オイルの冷却作用を改善するために、冷却通路は冷却通路カバーによって閉鎖され、この冷却通路カバーには冷却オイルを導入・排出するための開口が設けられている。また冷却通路カバーに、２部分から成る皿ばねの形を与えることも公知であり、この皿ばね（図１参照）はその外縁部２９で、外側の支持部として働く開放したリング壁２４の端面２３における凹設部２２に、軸方向のプレロード（Vorspannung）をかけられて固定され、かつ皿ばねの内縁部は、リングリブに内側の支持部２５として設けられた環状の段部２６に、軸方向のプレロードをかけられて固定されている。   It is known from German Patent No. 4208037 to provide in the region of the piston head of a piston for an internal combustion engine a cooling passage which is located radially outward and opens towards the piston skirt. In order to improve the cooling action of the cooling oil introduced into the cooling passage, the cooling passage is closed by a cooling passage cover, and the cooling passage cover is provided with an opening for introducing and discharging the cooling oil. It is also known to give the cooling passage cover the shape of a two-part disc spring, this disc spring (see FIG. 1) at its outer edge 29, the end face of the open ring wall 24 acting as an outer support. 23, the inner edge of the disc spring is fixed to the annular step portion 26 provided as the inner support portion 25 on the ring rib in the axial direction. The preload is fixed.

この公知の構成では、エンジン運転時に燃焼ガスの圧力によってピストンに対して、しかしながらまたピストンの往復動時にリング壁２４に対して作用する慣性力によって、リング壁２４とピストンベース体２８との間における相対運動（矢印２７参照）が発生する。その結果皿ばね３０は特に支持点３１，３２の領域においてリング壁２４に対して相対運動を生ぜしめ、これによって当該領域において皿ばね３０及び凹設部２２の損傷が惹起される。   In this known arrangement, the inertia between the ring wall 24 and the piston base body 28 is exerted on the piston by the pressure of the combustion gas during engine operation, but also by the inertial force acting on the ring wall 24 when the piston reciprocates. Relative motion (see arrow 27) occurs. As a result, the disc spring 30 causes relative movement with respect to the ring wall 24 particularly in the region of the support points 31 and 32, and this causes damage to the disc spring 30 and the recessed portion 22 in that region.

従来技術に基づいて公知の、２つの半円形の皿ばね半部から成る冷却通路カバーの別の欠点としては、冷却通路カバーから軸方向力及び半径方向力がリング壁２４に対して加えられる、ということが挙げられる。これらの力は、皿ばね半部の突き合わせ端部において最大であるので、軸方向力は当該領域においてピストンリング溝の非正弦形状（nichtsinusfoermig）の変形を引き起こし、このような変形に、その中に収容されたピストンリングは追従することができないので、特に、このようなピストンを備えた内燃機関のオイル消費が増大してしまう。半径方向に向けられた皿ばね半部の突き合わせ端部における最大力は、この場合、リング壁２４の横断面で見て楕円形の変形を生ぜしめ、このような変形はピストンの引っかかりもしくは食いつきを生ぜしめるおそれがある。   Another disadvantage of a cooling passage cover consisting of two half-circular disc spring halves known from the prior art is that axial and radial forces are applied to the ring wall 24 from the cooling passage cover. It can be mentioned. Since these forces are greatest at the butt end of the disc spring halves, the axial force causes a deformation of the non-sinusoidal shape of the piston ring groove in that region, and in such deformations, Since the accommodated piston ring cannot follow, the oil consumption of an internal combustion engine equipped with such a piston increases. The maximum force at the butt end of the belleville spring halves directed radially causes in this case an elliptical deformation as seen in the cross-section of the ring wall 24, such deformation causing piston catching or biting. There is a risk of giving birth.

ゆえに本発明の課題は、上に述べた従来技術における欠点を排除することである。   The object of the present invention is therefore to eliminate the disadvantages of the prior art described above.

この課題を解決するために本発明では、請求項１の特徴部に記載のように構成されている。本発明の別の有利な構成は請求項２に記載されている。   In order to solve this problem, the present invention is configured as described in the characterizing portion of claim 1. Another advantageous configuration of the invention is described in claim 2.

次に図面を参照しながら本発明の実施例を説明する。   Next, embodiments of the present invention will be described with reference to the drawings.

図１は、内燃機関用のピストンの冷却通路を閉鎖するための従来技術によるばね金属薄板を示す断面図であり、
図２は、本発明によるばね金属薄板を示す平面図であり、
図３は、図２のＩＩＩ−ＩＩＩ線に沿って本発明によるばね金属薄板を断面した図であり、
図４は、ピストンに取り付けた後における本発明によるばね金属薄板を示す図である。 FIG. 1 is a cross-sectional view showing a conventional spring metal sheet for closing a cooling passage of a piston for an internal combustion engine,
FIG. 2 is a plan view showing a spring metal thin plate according to the present invention,
FIG. 3 is a cross-sectional view of a spring metal thin plate according to the present invention along the line III-III in FIG.
FIG. 4 shows the spring metal sheet according to the invention after it has been attached to the piston.

図２及び図４には、内燃機関用のピストン８の冷却通路２０を閉鎖するためのリング状のばね金属薄板１が示されており、このばね金属薄板１は２つの半円形のばね金属薄板半部２，３から成っている。両ばね金属薄板半部２，３はそれぞれ一体成形部４，５を有しており、この一体成形部４，５は、ピストン８内に組み込まれたばね金属薄板１が回動することを防止するために働く。さらに両ばね金属薄板半部２，３は、冷却通路に対するオイルの導入・排出のために開口６，７を備えている。   FIGS. 2 and 4 show a ring-shaped spring metal sheet 1 for closing the cooling passage 20 of the piston 8 for the internal combustion engine. The spring metal sheet 1 includes two semicircular spring metal sheets. It consists of two and three halves. Both spring metal thin plate halves 2 and 3 have integrally formed portions 4 and 5, respectively, and the integrally formed portions 4 and 5 prevent the spring metal thin plate 1 incorporated in the piston 8 from rotating. Work for. Further, both spring metal thin plate halves 2 and 3 are provided with openings 6 and 7 for introducing and discharging oil to and from the cooling passage.

図３には、図２のＩＩＩ−ＩＩＩ線に沿ったばね金属薄板１の断面図が示されている。この図３には一体成形部４と開口７とが示されており、この図面から特に、ばね金属薄板１が弛緩された状態では浅いホッパの形をしていることが分かる。   FIG. 3 shows a cross-sectional view of the spring metal thin plate 1 along the line III-III in FIG. FIG. 3 shows the integrally formed portion 4 and the opening 7, and it can be seen from this drawing that, in particular, the spring metal thin plate 1 has a shallow hopper shape in the relaxed state.

図４には、ピストン８に取り付けられた後のばね金属薄板１が示されている。この図４から分かるように、金属薄板１はこの場合平らな位置を有しており、つまり金属薄板１は、図３に示されたホッパ状の位置に対してねじりを加えられている。これによってばね金属薄板１内において生じるねじり応力に起因して、ばね金属薄板１の半径方向内側の縁部領域１６は、ピストンベース体１４の半径方向外側に向かって延びる突出部１７のピストンヘッド側の表面、つまりに第１の支持部１０を形成する表面に、プレロードをかけられてで支持され、かつばね金属薄板１の半径方向外側の縁部領域１８は、リング部分１３の、ピストンヘッドとは反対側の下側面１５の階段状の凹設部１９によって形成される第２の支持部９に、プレロードをかけられて支持されており、これによりばね金属薄板１はピストン８において固定される。   FIG. 4 shows the spring metal sheet 1 after being attached to the piston 8. As can be seen from FIG. 4, the sheet metal 1 has a flat position in this case, that is, the sheet metal 1 is twisted with respect to the hopper-like position shown in FIG. Due to the torsional stress generated in the spring metal thin plate 1, the edge region 16 on the radially inner side of the spring metal thin plate 1 is located on the piston head side of the projecting portion 17 extending outward in the radial direction of the piston base body 14. , That is, the surface forming the first support 10, is supported by being preloaded and the radially outer edge region 18 of the spring sheet metal 1 is connected to the piston head of the ring part 13. Is supported by being preloaded on a second support portion 9 formed by a stepped concave portion 19 on the opposite lower side surface 15, whereby the spring metal thin plate 1 is fixed at the piston 8. .

ばね金属薄板１は外側半径１１（図２）を有しており、この外側半径１１は、ばね金属薄板１とピストン８との間に間隙１２（図４）が形成されるように寸法設定されている。これによって、ピストン８とばね金属薄板１との間における相対運動時に、間隙１２の領域においてばね金属薄板１及びピストン８の損傷を回避することができる。さらに支持部９，１０の面積は、ピストン８とばね金属薄板１との間における相対運動時に最小の摩耗しか生じないような大きさである。   The spring metal sheet 1 has an outer radius 11 (FIG. 2), which is dimensioned so that a gap 12 (FIG. 4) is formed between the spring metal sheet 1 and the piston 8. ing. This makes it possible to avoid damage to the spring metal sheet 1 and the piston 8 in the region of the gap 12 during relative movement between the piston 8 and the spring metal sheet 1. Further, the area of the support portions 9 and 10 is such that minimal wear occurs during relative movement between the piston 8 and the spring metal thin plate 1.

このような相対運動は、ピストン８に対して作用する燃料圧や、高回転数時にリング部分１３に対して作用する慣性力に基づいて発生し、これによってリング部分１３はピストンベース体１４に対して相対運動し、その結果リング部分１３及びピストンベース体１４の半径方向に対するばね金属薄板１の相対運動が惹起される。   Such a relative motion is generated based on the fuel pressure acting on the piston 8 and the inertial force acting on the ring portion 13 at a high rotational speed, whereby the ring portion 13 moves against the piston base body 14. As a result, relative movement of the spring metal sheet 1 with respect to the radial direction of the ring portion 13 and the piston base body 14 is caused.

組立て時に、両ばね金属薄板半部２，３はリング部分１３の、ピストンヘッドとは反対側の下側面１５に接触させられ、その半径方向内側において、ピストンヘッド２１に向かって作用する軸方向力にさらされ、これによって、ばね金属薄板半部２，３の半径方向内側の縁部領域１６が第１の支持部１０の上に接触するようなねじりを加えられる。その後でばね金属薄板半部２，３は、半径方向内側に向けられた力によって、図４に示されたポジションへと移動させられる。   During assembly, the two spring sheet metal halves 2 and 3 are brought into contact with the lower surface 15 of the ring portion 13 opposite to the piston head, and the axial force acting toward the piston head 21 on the radially inner side thereof. To which the torsion is applied such that the radially inner edge region 16 of the spring sheet metal halves 2, 3 contacts the first support 10. Thereafter, the spring sheet metal halves 2 and 3 are moved to the position shown in FIG. 4 by a force directed radially inward.

内燃機関用のピストンの冷却通路を閉鎖するための従来技術によるばね金属薄板を示す断面図である。It is sectional drawing which shows the spring metal thin plate by a prior art for closing the cooling passage of the piston for internal combustion engines. 本発明によるばね金属薄板を示す平面図である。It is a top view which shows the spring metal thin plate by this invention. 図２のＩＩＩ−ＩＩＩ線に沿って本発明によるばね金属薄板を断面した図である。FIG. 3 is a cross-sectional view of a spring metal thin plate according to the present invention along the line III-III in FIG. 2. ピストンに取り付けた後における本発明によるばね金属薄板を示す図である。FIG. 3 shows a spring metal sheet according to the present invention after being attached to a piston.

符号の説明Explanation of symbols

１ ばね金属薄板、 ２，３ ばね金属薄板半部、 ４，５ 一体成形部、 ６，７ 開口、 ８ ピストン、 ９ 第２の支持部、 １０ 第１の支持部、 １１ 外側半径、 １２ 間隙、 １３ リング部分、 １４ ピストンベース体、 １５ リング部分１３の下側面、 １６ ばね金属薄板１の半径方向内側の縁部領域、 １７ 突出部、 １８ ばね金属薄板１の半径方向外側の縁部領域、 １９ 階段状の凹設部、 ２０ 冷却通路、 ２１ ピストンヘッド、 ２２ 凹設部、 ２３ リング壁２４の端面、 ２４ リング壁、 ２５ 内側の支持部、 ２６ 段部、 ２７ 矢印、 ２８ ピストンベース体、 ２９ 皿ばね３０の外縁部、 ３０ 皿ばね、 ３１，３２ 支持点   DESCRIPTION OF SYMBOLS 1 Spring metal thin plate, 2, 3 Spring metal thin plate half part, 4, 5 Integrated molding part, 6, 7 Opening, 8 Piston, 9 2nd support part, 10 1st support part, 11 Outer radius, 12 Gap, 13 Ring portion, 14 Piston base body, 15 Lower surface of the ring portion 13, 16 Radial inner edge region of the spring metal thin plate 1, 17 Projection, 18 Radial outer edge region of the spring metal thin plate 1, 19 Stepped concave portion, 20 cooling passage, 21 piston head, 22 concave portion, 23 end face of ring wall 24, 24 ring wall, 25 inner support portion, 26 step portion, 27 arrow, 28 piston base body, 29 Outer edge of the disc spring 30, 30 disc spring, 31, 32

Claims (2)

内燃機関のピストン（８）のピストンヘッド（２１）の領域において半径方向外側に位置していてピストンヘッドとは反対側の下側面に向かって開放している冷却通路（２０）をカバーするための冷却通路カバーであって、該冷却通路カバーが、２つの半円形の半部（２，３）から成っているリング状のばね金属薄板（１）の形を有しており、該ばね金属薄板（１）の半径方向内側の縁部領域（１６）が、冷却通路（２０）を半径方向内側において画成するピストンベース体（１４）の、半径方向外側に向かって延びる突出部（１７）の上側面によって形成される第１の支持部（１０）に支持され、ばね金属薄板（１）の半径方向外側の縁部領域（１８）が、第２の支持部（９）にプレロードをかけられて支持されており、該第２の支持部（９）が、冷却通路（２０）の半径方向外側を画成するピストン（８）のリング部分（１３）の下側面（１５）における階段状の凹設部（１９）によって形成されている形式のものにおいて、
ばね金属薄板（１）の外側半径（１１）は次のように、すなわちばね金属薄板（１）の半径方向外側の端面と階段状の凹設部（１９）の半径方向外側の画成部との間に環状の間隙（１２）が生ぜしめられるように、寸法設定されており、
かつ第２の支持部（９）が少なくともほぼばね金属薄板（１）の厚さだけ、第１の支持部（１０）よりもピストンヘッド（２１）の近傍に位置するように設けられていて、その結果ピストン（８）への取付け後にばね金属薄板（１）が少なくともほぼ平らな位置を占めるようになっていることを特徴とする、内燃機関のピストン用の冷却通路カバー。 Covering a cooling passage (20) which is located radially outward in the region of the piston head (21) of the piston (8) of the internal combustion engine and which opens towards the lower side opposite to the piston head A cooling passage cover, the cooling passage cover having the shape of a ring-shaped spring metal sheet (1) consisting of two semicircular halves (2, 3), the spring metal sheet A radially inner edge region (16) of (1) of the protrusion (17) extending radially outward of the piston base body (14) defining the cooling passage (20) radially inward. Supported by the first support (10) formed by the upper side, the radially outer edge region (18) of the spring sheet metal (1) is preloaded on the second support (9). The second support portion ( ) Is formed by a stepped recess (19) in the lower surface (15) of the ring portion (13) of the piston (8) defining the radially outer side of the cooling passage (20) In
The outer radius (11) of the spring metal thin plate (1) is as follows, that is, the radially outer end face of the spring metal thin plate (1) and the radially outer defining portion of the stepped recess (19). Dimensioned to create an annular gap (12) between
And the second support part (9) is provided so as to be positioned closer to the piston head (21) than the first support part (10) by at least the thickness of the spring metal thin plate (1). As a result, the cooling passage cover for the piston of the internal combustion engine, characterized in that the spring metal sheet (1) occupies at least a substantially flat position after being mounted on the piston (8). 両方のばね金属薄板半部（２，３）が、半径方向外側に向かって延びる少なくとも１つの一体成形部（４，５）を有している、請求項１記載の冷却通路カバー。   The cooling passage cover according to claim 1, wherein both spring sheet metal halves (2, 3) have at least one integrally formed part (4, 5) extending radially outward.
JP2007508723A 2004-04-20 2005-04-19 Cooling passage cover for internal combustion engine pistons Active JP4598059B2 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004019011A DE102004019011A1 (en) 2004-04-20 2004-04-20 Cooling duct cover for a piston of an internal combustion engine
PCT/DE2005/000717 WO2005103473A1 (en) 2004-04-20 2005-04-19 Cooling channel covering for a piston of an internal combustion engine

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JP2007533904A true JP2007533904A (en) 2007-11-22
JP4598059B2 JP4598059B2 (en) 2010-12-15

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US (1) US7415959B2 (en)
EP (1) EP1738066B1 (en)
JP (1) JP4598059B2 (en)
KR (1) KR101246395B1 (en)
CN (1) CN1977103A (en)
BR (1) BRPI0510067B1 (en)
DE (1) DE102004019011A1 (en)
WO (1) WO2005103473A1 (en)

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US7762227B2 (en) * 2008-02-19 2010-07-27 Federal Mogul Corporation Coolable piston for internal combustion engine
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US7415959B2 (en) 2008-08-26
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